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Abstract:

A power train of an automatic transmission realizes nine forward speeds
and two reverse speeds. In the power train of this invention, an output
unit selectively receives reduced rotation speed from a speed reduction
unit or selectively receives rotation speed of an input shaft and
generates the nine forward speeds and two reverse speeds by operation of
five clutches and three brakes.

Claims:

1. A power train of an automatic transmission, comprising:a speed
reduction unit comprising a first operating member fixedly connected to a
transmission case, a second operating member always receiving rotation
speed of an input shaft, and a third operating member generating reduced
rotation speed by operation of the first and second operating members;an
output unit comprising a fourth operating member selectively receiving
the reduced rotation speed from the third operating member or selectively
connected to the transmission case, a fifth operating member selectively
receiving the rotation speed of the input shaft, selectively receiving
the reduced rotation speed from the third operating member, or
selectively connected to the transmission case, a sixth operating member
selectively connected to the transmission case, a seventh operating
member selectively receiving the reduced rotation speed from the third
operating member or selectively receiving the rotation speed of the input
shaft, and an eighth operating member generating nine forward speeds and
two reverse speeds by operation of the fourth, fifth, sixth, and seventh
operating members; anda plurality of friction members selectively
connecting the operating members of the speed reduction unit and the
output unit to the input shaft, other operating members, or the
transmission case therebetween.

2. The power train of claim 1, wherein the plurality of friction members
comprise:a first clutch selectively connecting the third operating member
to the seventh operating member;a second clutch selectively connecting
the third operating member to the fifth operating member;a third clutch
selectively connecting the seventh operating member to the input shalt;a
fourth clutch selectively connecting the fifth operating member to the
input shaft;a fifth clutch selectively connecting the third operating
member to the fourth operating member;a first brake selectively
connecting the fourth operating member to the transmission case;a second
brake selectively connecting the fifth operating member to the
transmission case; anda third brake selectively connecting the sixth
operating member to the transmission case.

3. The power train of claim 2, wherein the speed reduction unit is a first
planetary gear set having a first sun gear, a first ring gear, and a
first planet carrier as operating members thereof.

4. The power train of claim 3, wherein the first planetary gear set is a
single pinion planetary gear set, and wherein the first sun gear is
operated as the first operating member, the first ring gear is operated
as the second operating member, and the first planet carrier is operated
as the third operating member.

5. The power train of claim 4, wherein the output unit is a second
planetary gear set having a second sun gear, a third sun gear, a second
planet carrier, a second ring gear, and a third ring gear as operating
members thereof wherein the second planetary gear set is a compound
planetary gear set where a single pinion planetary gear set provided with
the second sun gear, the second planet carrier and the second ring gear,
and a double pinion planetary gear set provided with the third sun gear,
the second planet carrier and the third ring gear have the second planet
carrier in common.

6. The power train of claim 5, wherein the second sun gear is operated as
the fourth operating member, the second planet carrier is operated as the
fifth operating member, the second ring gear is operated as the sixth
operating member, the third sun gear is operated as the seventh operating
member, and the third ring gear is operated as the eighth operating
member.

7. The power train of claim 5, wherein the second planet carrier is
connected to a second pinion gear and a third pinion gear,wherein one end
of the second pinion gear is respectively engaged with the second ring
gear and the second sun gear, the other end of the second pinion gear is
engaged with the third ring gear and the third pinion gear, andthe third
pinion gear is engaged with the third sun gear.

8. The power train of claim 5, wherein the second planet carrier is
connected to a second pinion gear and a third pinion gear,wherein one end
of the second pinion gear is engaged with the second ring gear,a middle
portion of the second pinion gear is engaged with the second sun gear,the
other end of the second pinion gear is respectively engaged with the
third ring gear and the third pinion gear, andthe third pinion gear is
engaged with the third sun gear.

9. The power train of claim 4, wherein the output unit is a second
planetary gear set having a second sun gear, a second planet carrier, a
second ring gear, a third sun gear, a fourth sun gear, and a third ring
gear as operating members thereof wherein the second planetary gear set
is a compound planetary gear set where a single pinion planetary gear set
provided with the second sun gear, the second planet carrier, and the
second ring gear and a Ravingneaux planetary gear set provided with the
third sun gear, the fourth sun gear, the second planet carrier, and the
third ring gear have the second planet carrier in common.

10. The power train of claim 9, wherein the second sun gear is fixedly
connected to the third sun gear,wherein the fixedly connected second sun
gear and third sun gear are operated as the fourth operating member, the
second planet carrier is operated as the fifth operating member, the
second ring gear is operated as the sixth operating member, the fourth
sun gear is operated as the seventh operating member, and the third ring
rear is operated as the eighth operating member.

11. The power train of claim 10, wherein the second planet carrier is
connected to a second pinion gear, a third pinion gear and a fourth
pinion gear, and the second pinion gear is coaxially connected to the
third pinion gear,wherein the second pinion gear is respectively engaged
with the second ring gear and the second sun gear,one end of the third
pinion gear is engaged with the third sun gear,the other end of the third
pinion gear is respectively engaged with the third ring gear and the
fourth pinion gear, andthe fourth pinion gear is engaged with the fourth
sun gear.

Description:

CROSS-REFERENCE TO RELATED APPLICATION

[0001]This application claims priority to and the benefit of Korean Patent
Application No. 10-2007-0111537, filed in the Korean Intellectual
Property Office on Nov. 2, 2007, the entire contents of which are
incorporated herein by reference.

BACKGROUND OF THE INVENTION

[0002](a) Field of the Invention

[0003]The present invention relates to a power train of an automatic
transmission. More particularly, the present invention relates to a power
train of an automatic transmission that realizes nine forward speeds and
two reverse speeds.

[0004](b) Description of the Related Art

[0005]A typical shift mechanism of an automatic transmission utilizes a
combination of a plurality of planetary gear sets. A power train of such
an automatic transmission changes rotational speed and torque received
from a torque converter of the automatic transmission, and accordingly
transmits the changed torque to an output shaft.

[0006]It is well known that when a transmission realizes a greater number
of shift speeds, speed ratios of the transmission can be more optimally
designed, and therefore a vehicle can have economical fuel mileage and
better performance. For that reason, an automatic transmission that is
able to realize more shift speeds is under continuous investigation.

[0007]In addition, with the same number of speeds, features of a power
train, such as durability, efficiency in power transmission, and size,
depend a lot on the layout of the combined planetary gear sets.
Therefore, designs for a combining structure of a power train are also
under continuous investigation.

[0008]A manual transmission that has too many shift-speeds causes
inconvenience to a driver. Therefore, the advantageous features of having
more shift-speeds are more important in an automatic transmission because
an automatic transmission automatically controls the shifting operations.

[0009]The above information disclosed in this Background section is only
for enhancement of understanding of the background of the invention and
therefore it may contain information that does not form the prior art
that is already known in this country to a person of ordinary skill in
the art.

SUMMARY OF THE INVENTION

[0010]The present invention has been made in an effort to provide a power
train of an automatic transmission having advantages of improving power
delivery performance and reducing fuel consumption as a consequence of
realizing nine forward speeds and two reverse speeds by using three or
four planetary gear sets, five clutches, and three brakes.

[0011]A power train of an automatic transmission according to exemplary
embodiments of the present invention may include: a speed reduction unit
including a first operating member fixedly connected to a transmission
case, a second operating member always receiving rotation speed of an
input shaft and a third operating member generating reduced rotation
speed by operation of the first and second operating members; an output
unit including a fourth operating member selectively receiving the
reduced rotation speed from the third operating member or selectively
connected to the transmission case, a fifth operating member selectively
receiving the rotation speed of the input shaft, selectively receiving
the reduced rotation speed from the third operating member, or
selectively connected to the transmission case, a sixth operating member
selectively connected to the transmission case, a seventh operating
member selectively receiving the reduced rotation speed from the third
operating member or selectively receiving the rotation speed of the input
shaft, and an eighth operating member generating nine forward speeds and
two reverse speeds by operation of the fourth, fifth, sixth, and seventh
operating members; and a plurality of friction members selectively
connecting operating members of the speed reduction unit and the output
unit to the input shaft, other operating members, or the transmission
case.

[0012]The plurality of friction members may include: a first clutch
selectively connecting the third operating member to the seventh
operating member; a second clutch selectively connecting the third
operating member to the fifth operating member; a third clutch
selectively connecting the seventh operating member to the input shaft; a
fourth clutch selectively connecting the fifth operating member to the
input shalt; a fifth clutch selectively connecting the third operating
member to the fourth operating member; a first brake selectively
connecting the fourth operating member to the transmission case; a second
brake selectively connecting the fifth operating member to the
transmission case; and a third brake selectively connecting the sixth
operating member to the transmission case.

[0013]The speed reduction unit may be a first planetary gear set having a
first sun gear, a first ring gear, and a first planet carrier as
operating members thereof.

[0014]The first planetary gear set may be a single pinion planetary gear
set, wherein the first sun gear is operated as the first operating
member, the first ring gear is operated as the second operating member,
and the first planet carrier is operated as the third operating member.

[0015]The output unit of a power train according to the first and second
exemplary embodiments of the present invention may be a second planetary
gear set having a second sun gear, a third sun gear, a second planet
carrier, a second ring gear, and a third ring gear as operating members
thereof, wherein the second planetary gear set is a compound planetary
gear set where a single pinion planetary gear set provided with the
second sun gear, the second planet carrier, and the second ring gear and
a double pinion planetary gear set provided with the third sun gear, the
second planet carrier, and the third ring gear have the second planet
carrier in common.

[0016]The second sun gear may be operated as the fourth operating member,
the second planet carrier may be operated as the fifth operating member,
the second ring gear may be operated as the sixth operating member, the
third sun gear may be operated as the seventh operating member, and the
third ring gear may be operated as the eighth operating member.

[0017]According to the first exemplary embodiment of the present
invention, the second planet carrier is connected to a second pinion gear
and a third pinion gear, wherein one end of the second pinion gear is
respectively engaged with the second ring gear and the second sun gear,
the other end of the second pinion gear is engaged with the third ring
gear and the third pinion gear, and the third pinion gear is engaged with
the third sun gear.

[0018]According to the second exemplary embodiment of the present
invention, the second planet carrier is connected to a second pinion gear
and a third pinion gear, wherein one end of the second pinion gear is
engaged with the second ring gear, a middle portion of the second pinion
gear is engaged with the second sun gear, the other end of the second
pinion gear is respectively engaged with the third ring gear and the
third pinion gear, and the third pinion gear is engaged with the third
sun gear.

[0019]The output unit of a power train according to the third exemplary
embodiment of the present invention may be a second planetary gear set
having a second sun gear, a second planet carrier, a second ring gear, a
third sun gear, a fourth sun gear, and a third ring gear as operating
members thereof, wherein the second planetary gear set is a compound
planetary gear set where a single pinion planetary gear set provided with
the second sun gear, the second planet carrier, and the second ring gear
and a Ravingneaux planetary gear set provided with the third sun gear,
the fourth sun gear, the second planet carrier, and the third ring gear
have the second planet carrier in common.

[0020]The second sun gear may be fixedly connected to the third sun gear,
wherein the fixedly connected second sun gear and third sun gear are
operated as the fourth operating member, the second planet carrier is
operated as the fifth operating member, the second ring gear is operated
as the sixth operating member, the fourth sun gear is operated as the
seventh operating member, and the third ring gear is operated as the
eighth operating member.

[0021]The second planet carrier may be connected to a second pinion gear,
a third pinion gear, and a fourth pinion gear, and the second pinion gear
is coaxially connected to the third pinion gear, wherein the second
pinion gear is respectively engaged with the second ring gear and the
second sun gear, one end of the third pinion gear is engaged with the
third sun gear, the other end of the third pinion gear is respectively
engaged with the third ring gear and the fourth pinion gear, and the
fourth pinion gear is engaged with the fourth sun gear.

[0022]The above features and advantages of the present invention will be
apparent from or are set forth in more detail in the accompanying
drawings, which are incorporated in and form a part of this
specification, and the following Detailed Description of the invention,
which together serve to explain by way of example the principles of the
present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

[0023]The above and other features of the present invention will now be
described in detail with reference to certain exemplary embodiments
thereof illustrated the accompanying drawings which are given hereinbelow
by way of illustration only, and thus are not limitative of the present
invention, and wherein:

[0024]FIG. 1 is a schematic diagram of a power train of an automatic
transmission according to the first exemplary embodiment of the present
invention.

[0025]FIG. 2 is an operational chart for a power train of an automatic
transmission according to the first exemplary embodiment of the present
invention.

[0026]FIG. 3 is a lever diagram showing shifting processes from a first
forward speed to an ninth forward speed and two reverse speeds in a power
train of an automatic transmission according to the first exemplary
embodiment of the present invention.

[0027]FIG. 4 is a schematic diagram of a power train of an automatic
transmission according to the second exemplary embodiment of the present
invention.

[0028]FIG. 5 is an operational chart for a power train of an automatic
transmission according to the second exemplary embodiment of the present
invention.

[0029]FIG. 6 is a lever diagram showing shifting processes from a first
forward speed to an ninth forward speed and two reverse speeds in a power
train of an automatic transmission according to the second exemplary
embodiment of the present invention.

[0030]FIG. 7 is a schematic diagram of a power train of an automatic
transmission according to the third exemplary embodiment of the present
invention.

[0031]FIG. 8 is an operational chart for a power train of an automatic
transmission according to the third exemplary embodiment of the present
invention.

[0032]FIG. 9 is a lever diagram showing shifting processes from a first
forward speed to an ninth forward speed and two reverse speeds in a power
train of an automatic transmission according to the third exemplary
embodiment of the present invention.

[0033]It should be understood that the appended drawings are not
necessarily to scale, presenting a somewhat simplified representation of
various preferred features illustrative of the basic principles of the
invention. The specific design features of the present invention as
disclosed herein, including, for example, specific dimensions,
orientations, locations, and shapes will be determined in part by the
particular intended application and use environment.

[0034]In the figures, reference numbers refer to the same or equivalent
parts of the present invention throughout the several figures of the
drawing.

DETAILED DESCRIPTION OF THE EMBODIMENTS

[0035]Thereinafter reference will now be made in detail to various
embodiments of the present invention, examples of which are illustrated
in the accompanying drawings and described below. While the invention
will be described in conjunction with exemplary embodiments, it will be
understood that present description is not intended to limit the
invention to those exemplary embodiments. On the contrary, the invention
is intended to cover not only the exemplary embodiments, but also various
alternatives, modifications, equivalents and other embodiments, which may
be included within the spirit and scope of the invention as defined by
the appended claims.

[0036]Exemplary embodiments of the present invention will hereinafter be
described in detail with reference to the accompanying drawings.

[0037]As shown in FIG. 1 to FIG. 9, power trains of an automatic
transmission according to exemplary embodiments of the present invention
include an input shaft 100, an output gear 200, a transmission case 300,
a speed reduction unit PG1, an output unit PG2, and a plurality of
friction members C1, C2, C3, C4, C5, B1, B2, and B3.

[0040]The speed reduction unit PG1 includes first, second, and third
operating members. The speed reduction unit PG1 receives torque from the
input shaft 100 and transmits reduced rotation speed to the output unit
PG2 by operation of the first, second, and third operating members. The
first operating member is fixedly connected to the transmission case 300
and is always stopped. The second operating member is fixedly connected
to the input shaft 100 and always rotates with the same rotation speed as
the input shaft 100. The third operating member generates the reduced
rotation speed by operation of the first and second operating members.

[0041]The output unit PG2 includes fourth, fifth, sixth, seventh, and
eighth operating members. The output unit PG2 receives the reduced
rotation speed from the speed reduction unit PG1 or receives the torque
from the input shaft 100, and transmits nine forward speeds and two
reverse speeds to the output gear 200. The fourth operating member
selectively receives the reduced rotation speed from the third operating
member or is selectively connected to the transmission case 300 to be
selectively stopped. The fifth operating member is selectively connected
to the input shaft 100 and selectively receives the rotation speed of the
input shaft 100, selectively receives the reduced rotation speed from the
third operating member, or is selectively connected to the transmission
case 300 to be selectively stopped. The sixth operating member is
selectively connected to the transmission case 300 to be stopped. The
seventh operating member selectively receives the reduced rotation speed
from the third operating member or selectively receives the rotation
speed of the input shaft 100. The eighth operating member is fixedly
connected to the output gear 200 and outputs the nine forward speeds and
two reverse speeds generated by operation of the fourth, fifth, sixth,
and seventh operating members to the output gear 200.

[0042]The plurality of friction members connect operating members of the
speed reduction unit PG1 and the output unit PG2 to the input shaft 100,
other operating members, or the transmission case 300. The plurality of
friction members include first, second, third, fourth, and fifth clutches
C1, C2, C3, C4, and C5 and first, second, and third brakes B1, B2, and
B3. The first clutch C1 selectively connects the third operating member
to the seventh operating member to selectively transmit the reduced
rotation speed of the third operating member to the seventh operating
member. The second clutch C2 selectively connects the third operating
member to the fifth operating member to selectively transmit the reduced
rotation speed of the third operating member to the fifth operating
member. The third clutch C3 selectively connects the seventh operating
member to the input shaft 100 to selectively transmit the rotation speed
of the input shaft 100 to the seventh operating member. The fourth clutch
C4 selectively connects the fifth operating member to the input shaft 100
to selectively transmit the rotation speed of the input shaft 100 to the
fifth operating member. The fifth clutch C5 selectively connects the
third operating member to the fourth operating member to selectively
transmit the reduced rotation speed of the third operating member to the
fourth operating member. The first brake B1 selectively connects the
fourth operating member to the transmission case 300 to selectively stop
the fourth operating member. The second brake B2 selectively connects the
fifth operating member to the transmission case 300 to selectively stop
the fifth operating member. The third brake B3 selectively connects the
sixth operating member to the transmission case 300 to selectively stop
the sixth operating member.

[0043]Hereinafter, referring to FIG. 1, the power train of an automatic
transmission according to the first exemplary embodiment of the present
invention will be described in detail.

[0044]As shown in FIG. 1, according to the first exemplary embodiment of
the present invention, the speed reduction unit PG1 is a first planetary
gear set having a first sun gear S1, a first ring gear R1, and a first
planet carrier PC1 as operating members thereof. The first planetary gear
set is a single pinion planetary gear set. A first pinion gear P1, being
engaged with the first ring gear R1 and the first sun gear S1, is
connected to the first planet carrier PC1. In addition, the first sun
gear S1 is operated as the first operating member, the first ring gear R1
is operated as the second operating member, and the first planet carrier
PC1 is operated as the third operating member.

[0045]The output unit PG2 is a second planetary gear set having a second
sun gear S2, a third sun gear S3, a second planet carrier PC2, a second
ring gear R2, and a third ring gear R3 as operating members thereof. The
second planetary gear set is a compound planetary gear set where a single
pinion planetary gear set provided with the second sun gear S2, the
second planet carrier PC2, and the second ring gear R2 and a double
pinion planetary gear set provided with the third sun gear S3, the second
planet carrier PC2, and the third ring gear R3 have the second planet
carrier PC2 in common.

[0046]The second planet carrier PC2 is connected to a second pinion gear
P2 and a third pinion gear P3 in common. One end of the second pinion
gear P2 is respectively engaged with the second ring gear R2 and the
second sun gear S2, and the other end of the second pinion gear P2 is
respectively engaged with the third ring gear R3 and the third pinion
gear P3. In addition, the third pinion gear P3 is engaged with the third
sun gear S3.

[0047]Further, the second sun gear S2 is operated as the fourth operating
member, the second planet carrier PC2 is operated as the fifth operating
member, the second ring gear R2 is operated as the sixth operating
member, the third sun gear S3 is operated as the seventh operating
member, and the third ring gear R3 is operated as the eighth operating
member.

[0048]Hereinafter, referring to FIG. 2, operation of the power train of an
automatic transmission according to the first exemplary embodiment of the
present invention will be described.

[0049]As shown in FIG. 2, according to the first exemplary embodiment of
the present invention, the first clutch C1 and the third brake B3 are
applied in a first forward speed D1, the first clutch C1 and the second
brake B2 are applied in a second forward speed D2, the first clutch C1
and the first brake B1 are applied in a third forward speed D3, the first
clutch C1 and the second clutch C2 are applied in a fourth forward speed
D4, the second clutch C2 and the third clutch C3 are applied in a fifth
forward speed D5 the third clutch C3 and the fifth clutch C5 are applied
in a sixth forward speed D6, the third clutch C3 and the fourth clutch C4
are applied in a seventh forward speed D7, the fourth clutch C4 and the
fifth clutch C5 are applied in a eighth forward speed D8, and the fourth
clutch C4 and the first brake B1 are applied in a ninth forward speed D9.

[0050]In addition, the fifth clutch C5 and the third brake B3 are applied
in a first reverse speed REV1, and the fifth clutch C5 and the second
brake B2 are applied in a second reverse speed REV2.

[0051]Hereinafter, formation of the nine forward speeds and two reverse
speeds in the power train of an automatic transmission according to the
first exemplary embodiment of the present invention will be described in
detail.

[0052]As shown in FIG. 3, the power train of an automatic transmission
according to the first exemplary embodiment of the present invention
includes one single pinion planetary gear set and one compound planetary
gear set. Therefore, operating members of the power train according to
the first exemplary embodiment of the present invention are represented
as eight nodes in the lever diagram.

[0053]Accordingly, the first sun gear S1 is set as a first node N1, the
first planet carrier PC1 is set as a second node N2, the first ring gear
R1 is set as a third node N3, the second sun gear S2 is set as a fourth
node N4, the second planet carrier PC2 is set as a fifth node N5, the
second ring gear R2 is set as a sixth node N6, the third ring gear R3 is
set as a seventh node N7, and the third sun gear S3 is set as a eighth
node N8.

[0054]As described above, the first sun gear S1 is always connected to the
transmission case 300, and thus the first node N1 is always stopped. In
addition, the first ring gear R1 is always connected to the input shaft
100, and thus the third node N3 rotates with the same rotation speed as
the input shaft 100. Therefore, the second node N2 of the first planet
carrier PC1 outputs the reduced rotation speed.

[0055]The second sun gear S2 is selectively connected to the first planet
carrier PC1 by the fifth clutch C5 and is selectively connected to the
transmission case 300 by the first brake B1. Therefore, the fourth node
N4 of the second sun gear S2 rotates with the reduced rotation speed
output from the first planet carrier PC1 by operation of the fifth clutch
C5 or is stopped by operation of the first brake B1.

[0056]The second planet carrier PC2 is selectively connected to the input
shaft 100 by operation of the fourth clutch C4, is selectively connected
to the first planet carrier PC1 by operation of the second clutch C2, or
is selectively connected to the transmission case 300 by operation of the
second brake B2. Therefore, the fifth node N5 of the second planet
carrier PC2 rotates with the same rotation speed as the input shaft 100
by operation of the fourth clutch C4, rotates with the reduced rotation
speed output from the first planet carrier PC1 by operation of the second
clutch C2, or is stopped by operation of the second brake B2.

[0057]The second ring gear R2 is selectively connected to the transmission
case 300 by operation of the third brake B3, and thus the sixth node N6
of the second ring gear R2 is stopped by operation of the third brake B3.

[0058]The seventh node N7 of the third ring gear R3 is always connected to
the output gear 200 and operates as an output member.

[0059]The third sun gear S3 is selectively connected to the input shaft
100 by operation of the third clutch C3 and is selectively connected to
the first planet carrier PC1 by operation of the first clutch C1.
Therefore, the eighth node N8 of the third sun gear S3 rotates with the
same rotation speed as the input shaft 100 by operation of the third
clutch C3 or rotates with the reduced rotation speed output from the
first planet carrier PC1 by operation of the first clutch C1.

[0060]Hereinafter, processes for realizing respective shift speeds in the
power train of an automatic transmission according to the first exemplary
embodiment of the present invention will be described in detail,
referring to FIG. 3.

[0061]In the first forward speed D1, the eighth node N8 rotates with the
reduced rotation speed output from the first planet carrier PC1 by the
operation of the first clutch C1. In addition, the sixth node N6 is
stopped by the operation of the third brake B3. Therefore, the first
forward speed D1 is generated at the seventh node N7.

[0062]In the second forward speed D2, the eighth node Ng rotates with the
reduced rotation speed output from the first planet carrier PC1 by the
operation of the first clutch C1. In addition, the fifth node N5 is
stopped by the operation of the second brake B2. Therefore, the second
forward speed D2 is generated at the seventh node N7.

[0063]In the third forward speed D3, the eighth node N8 rotates with the
reduced rotation speed output from the first planet carrier PC1 by the
operation of the first clutch C1. In addition, the fourth node N4 is
stopped by the operation of the first brake B1. Therefore, the third
forward speed D3 is generated at the seventh node N7.

[0064]In the fourth forward speed D4, the eighth node Ng rotates with the
reduced rotation speed output from the first planet carrier PC1 by the
operation of the first clutch C1. In addition, the fifth node N5 also
rotates with the reduced rotation speed output from the first planet
carrier PC1 by the operation of the second clutch C2. Therefore, the
fourth forward speed D4 is generated at the seventh node N7.

[0065]In the fifth forward speed D5, the fifth node N5 rotates with the
reduced rotation speed output from the first planet carrier PC1 by the
operation of the second clutch C2. In addition, the eighth node N8
rotates with the same rotation speed as the input shall 100 by the
operation of the third clutch C3. Therefore, the fifth forward speed D5
is generated at the seventh node N7.

[0066]In the sixth forward speed D6, the eighth node N8 rotates with the
same rotation speed as the input shalt 100 by the operation of the third
clutch C3. In addition, the fourth node N4 rotates with the reduced
rotation speed output from the first planet carrier PC1 by the operation
of the fifth clutch C5. Therefore, the sixth forward speed D6 is
generated at the seventh node N7.

[0067]In the seventh forward speed D7, the eighth node N8 rotates with the
same rotation speed as the input shalt 100 by the operation of the third
clutch C3. In addition, the fifth node N5 also rotates with the same
rotation speed as the input shaft 100 by the operation of the fourth
clutch C4. Therefore, the seventh forward speed D7 is generated at the
seventh node N7.

[0068]In the eighth forward speed D8, the fifth node N5 rotates with the
same rotation speed as the input shaft 100 by the operation of the fourth
clutch C4. In addition, the fourth node N4 rotates with the reduced
rotation speed output from the first planet carrier PC1 by the operation
of the fifth clutch C5. Therefore, the eighth forward speed D8 is
generated at the seventh node N7.

[0069]In the ninth forward speed D9, the fifth node N5 rotates with the
same rotation speed as the input shaft 100 by the operation of the fourth
clutch C4. In addition, the fourth node N4 is stopped by the operation of
the first brake B1. Therefore, the ninth forward speed D9 is generated at
the seventh node N7.

[0070]In the first reverse speed REV1 the fourth node N4 rotates with the
reduced rotation speed output front the first planet carrier PC1 by the
operation of the fifth clutch C5. In addition the sixth node N6 is
stopped by the operation of the third brake B3. Therefore, the first
reverse speed REV1 is generated at the seventh node N7.

[0071]In the second reverse speeds REV2, the fourth node N4 rotates with
the reduced rotation speed output from the first planet carrier PC1 by
the operation of the fifth clutch C5. In addition, the filth node N5 is
stopped by the operation of the second brake B2. Therefore, the second
reverse speed REV2 is generated at the seventh node N7.

[0072]Hereinafter, power trains of an automatic transmission according to
other exemplary embodiments of the present inventions will be described.
The power trains of an automatic transmission according to other
exemplary embodiments of the present inventions are similar to the power
train of an automatic transmission according to the first exemplary
embodiment of the present invention. Therefore, only differences between
the first embodiment of the present invention and the other embodiments
of the present invention will be described.

[0073]As shown in FIG. 4, according to the second exemplary embodiment of
the present invention, the speed reduction unit PG1 is a first planetary
gear set having a first sun gear S1, a first ring gear R1, and a first
planet carrier PC1 as operating members thereof. The first planetary gear
set is a single pinion planetary gear set. A first pinion gear P1, being
engaged with the first ring gear R1 and the first sun gear S1, is
connected to the first planet carrier PC1. In addition, the first sun
gear S1 is always connected to the transmission case 300 and is operated
as the first operating member, the first ring gear R1 is operated as the
second operating member, and the first planet carrier PC1 is operated as
the third operating member.

[0074]The output unit PG2 is a second planetary gear set having a second
sun gear S2, a third sun gear S3, a second planet carrier PC2, a second
ring gear R2, and a third ring gear R3 as operating members thereof. The
second planetary gear set is a compound planetary gear set where a single
pinion planetary gear set provided with the second sun gear S2, the
second planet carrier PC2, and the second ring gear R? and a double
pinion planetary gear set provided with the third sun gear S8, the second
planet carrier PC2, and the third ring gear R3 have the second planet
carrier PC2 in common with the single pinion planetary gear set.

[0075]The second planet carrier PC2 is connected to the second pinion gear
P2 and the third pinion gear P3. One end of the second pinion gear P2 is
engaged with the second ring gear R2, a middle portion of the second
pinion gear P2 is engaged with the second sun gear S2, and the other end
of the second pinion gear P1 is respectively engaged with the third ring
gear R3 and the third pinion gear P3. In addition, the third pinion gear
P3 is engaged with the third sun gear S3.

[0076]Further, the second sun gear S2 is operated as the fourth operating
member, the second planet carrier PC2 is operated as the fifth operating
member, the second ring gear R2 is operated as the sixth operating
member, the third sun gear S3 is operated as the seventh operating
member, and the third ring gear R3 is operated as the eighth operating
member.

[0077]Operation, shifting processes, and formation of each speed of the
power train according to the second exemplary embodiment of the present
invention as shown in FIGS. 5 and 6 are similar to those of the power
train according to the first embodiment of the present invention, and may
be easily obtained by a person skilled in the art based on the teachings
herein. Thus, a detailed explanation thereof will be omitted.

[0078]As shown in FIG. 7, according to the third exemplary embodiment of
the present invention, the speed reduction unit PG1 is a first planetary
gear set having a first sun gear S1, a first ring gear R1, and a first
planet carrier PC1 as operating members thereof. The first planetary gear
set is a single pinion planetary gear set. A first pinion gear P1, being
engaged with the first ring gear R1 and the first Sun gear S1, is
connected to the first planet carrier PC1. In addition, the first sun
gear S1 is always connected to the transmission case 300 and is operated
as the first operating member, the first ring gear R1 is operated as the
second operating member, and the first planet carrier PC1 is operated as
the third operating member.

[0079]The output unit PG2 is a second planetary gear set having a second
sun gear S2, a third sun gear S3, a fourth sun gear S4, a second planet
carrier PC2, a second ring gear R2, and a third ring gear R3 as operating
members thereof. The second planetary gear set is a compound planetary
gear set where a single pinion planetary gear set provided with the
second sun gear S2, the second planet carrier PC2, and the second ring
gear R2 and a Ravingneaux planetary gear set provided with the third sun
gear S3, the fourth sun gear 84, the second planet carrier PC2, and the
third ring gear R3 have the second planet carrier PC2 in common.

[0080]The second planet carrier PC2 is connected to the second pinion gear
P2, the third pinion gear P3, and the fourth pinion gear P4, and the
second pinion gear P2 is coaxially connected to the third pinion gear P3.
The second pinion gear P2 is respectively engaged with the second ring
gear R2 and the second sun gear S2. One end of the third pinion gear P3
is engaged with the third sun gear S3, and the other end of the third
pinion gear P3 is respectively engaged with the third ring gear R3 and
the fourth pinion gear P4. The fourth pinion gear P4 is engaged with the
fourth sun gear S4.

[0081]In addition, the second sun gear S2 is fixedly connected to the
third sun gear S3. The fixedly connected second sun gear S2 and the third
sun gear S3 are operated as the fourth operating member, the second
planet carrier PC2 is operated as the filth operating member, the second
ring gear R2 is operated as the sixth operating member, the fourth sun
gear S4 is operated as the seventh operating member, and the third ring
gear R3 is operated as the eighth operating member.

[0082]Operation, shifting processes, and formation of each speed of the
power train according to the third exemplary embodiment of the present
invention as shown in FIGS. 8 and 9 are similar to those of the power
train according to the first embodiment of the present invention, and may
be easily obtained by a person skilled in the art based on the teachings
herein. Thus, a detailed explanation thereof will be omitted.

[0083]According to the exemplary embodiments of the present invention,
nine forward speeds and two reverse speeds may be realized by using three
or four planetary gear sets, five clutches, and three brakes.

[0084]In addition, since many shift speeds are realized, torque of an
engine may be effectively used, power delivery performance may be
improved, and fuel consumption may be reduced.

[0085]The forgoing descriptions of specific exemplary embodiments of the
present invention have been presented for purposes of illustration and
description. They are not intended to be exhaustive or to limit the
invention to the precise forms disclosed, and obviously many
modifications and variations are possible in light of the above
teachings. The exemplary embodiment were chosen and described in order to
explain certain principles of the invention and their practical
application, to thereby enable others skilled in the ant to make and
utilize various exemplary embodiments of the present invention) as well
as various alternatives and modifications thereof. It is intended that
technical spirit and scope of the present invention be defined by the
Claims appended hereto and their equivalents.